CN100491866C - Multistage-cascaded compression type heat pump set under large temperature difference - Google Patents
Multistage-cascaded compression type heat pump set under large temperature difference Download PDFInfo
- Publication number
- CN100491866C CN100491866C CNB200710099607XA CN200710099607A CN100491866C CN 100491866 C CN100491866 C CN 100491866C CN B200710099607X A CNB200710099607X A CN B200710099607XA CN 200710099607 A CN200710099607 A CN 200710099607A CN 100491866 C CN100491866 C CN 100491866C
- Authority
- CN
- China
- Prior art keywords
- condenser
- stage
- evaporator
- throttling arrangement
- level
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
- 230000006835 compression Effects 0.000 title claims abstract description 33
- 238000007906 compression Methods 0.000 title claims abstract description 33
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 76
- 239000003507 refrigerant Substances 0.000 claims description 49
- 230000008676 import Effects 0.000 claims description 4
- 239000007788 liquid Substances 0.000 description 29
- 238000001704 evaporation Methods 0.000 description 17
- 229920006395 saturated elastomer Polymers 0.000 description 16
- 230000008020 evaporation Effects 0.000 description 14
- 238000009833 condensation Methods 0.000 description 10
- 230000005494 condensation Effects 0.000 description 10
- 238000001816 cooling Methods 0.000 description 8
- 238000010521 absorption reaction Methods 0.000 description 7
- 230000007306 turnover Effects 0.000 description 6
- 238000010438 heat treatment Methods 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 230000002427 irreversible effect Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 125000004122 cyclic group Chemical group 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 239000008400 supply water Substances 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000007701 flash-distillation Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000010842 industrial wastewater Substances 0.000 description 1
- 239000002352 surface water Substances 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
- 230000009897 systematic effect Effects 0.000 description 1
Images
Landscapes
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
This invention relates to a multi-stage serial large temperature-difference compression thermal pump set composed of multiple stages of condensers, evaporators, a compressor and a related throttle device and connection pipelines, in which the waterway systems of the condensers of each stage and evaporators are serial to form a connected in-out system of waterway, pipelines of cold-producing medium of the adjacent condensers are serial by the throttle device, the condenser of the last stage is connected with the evaporator of the first stage by the compressor to form a channel of cold-producing medium.
Description
Technical field
The invention belongs to a kind of source pump that is used for heating, refrigeration, heat supply water, particularly a kind of efficient compression type heat pump assembly that can all obtain the big import and export temperature difference at hot and cold source.
Background technology
At present, various heat pump assemblies have been widely used in various heating, refrigeration and the hot water supply system, wherein in, in the large-scale heat supplying air conditioning system, water one water compression heat pump has obtained using comparatively widely, for example adopts underground water, surface water or industrial waste water etc. to be the heat pump water chiller-heater unit of low-temperature heat source.In order to reduce conveying energy consumption, save the water yield, to reduce the distributing system initial cost, general water side is easily taked the big temperature difference, low discharge operation.Under the certain situation of inflow temperature, the big temperature difference, low discharge mean the rising of hot water supply water temperature and the reduction of cold water leaving water temperature, to heat pump assembly commonly used, can cause the rising of condensing pressure and the reduction of evaporating pressure, cause systematic function coefficient (COP) to reduce, efficiency of energy utilization reduces.
Summary of the invention
At the problems referred to above, the invention provides and a kind ofly all take the big temperature difference compression type heat of the plural serial stage pump assembly of the big temperature difference, low discharge operation at hot and cold source, its efficiency of energy utilization is compared with conventional heat pump assembly be significantly improved.
Technical scheme of the present invention is as follows:
The big temperature difference compression type heat of a kind of plural serial stage pump assembly is characterized in that: this unit is made up of two-stage or the condenser more than the two-stage, evaporimeter, compressor and corresponding throttling arrangement and connecting line; Condenser hot water lines at different levels connect mutually, are about in the condensers at different levels in order to the water inlet pipe of heat exchange and the turnover loop of a connection of outlet pipe front and back section series connection formation mutually, a shared water system; Evaporimeter cold water pipelines at different levels are connected mutually, are about in the evaporimeters at different levels in order to the water inlet pipe of heat exchange and the turnover loop of a connection of outlet pipe front and back section series connection formation mutually, a shared water system; Be connected in series by throttling arrangement between the adjacent condenser refrigerant line, last condenser stage is connected by throttling arrangement with first evaporator; Also be connected in series between the adjacent evaporator refrigerant pipeline by throttling arrangement; Be connected by compressor with between one-level evaporimeter and the condenser, form refrigerant passage.
Technical characterictic of the present invention also is: between last condenser stage and first evaporator economizer is set, flash gas path pipeline is connected with the intergrade of final stage compressor, described economizer adopts open type economizer or closed economy device.
The present invention compared with prior art, have the following advantages and the high-lighting effect: the present invention can strengthen hot water and the cold water temperature difference at the heat pump import and export, make it by the big temperature difference, low discharge operation, and the coefficient of performance of source pump still remains on one than higher level, so the system synthesis efficiency of energy utilization improves than ordinary hot pump assembly greatly with economy.The improvement of plural serial stage source pump performance is mainly reflected in: the first, and the cold water temperature step reduces, and hot water temperature's step raises, and has reduced the heat transfer temperature difference of evaporation ends and condensation end, has reduced irreversible heat transfer loss; The second, the series connection of condenser cold-producing medium, condensate temperature reduces one by one, fully reclaims the cold-producing medium heat; The 3rd, refrigerant liquid is shwoot cooling step by step in evaporimeters at different levels, and pressure step reduces, and has increased refrigerating capacity and system energy efficiency; The 4th, adopt the mode of plural serial stage, can choose different heat pump units, guarantee that every compressor moves under its efficient operating mode according to the operating mode of different temperature rise sections, and can regulate hot water or cold water's leaving water temperature by control compressor operating platform number, satisfy user's requirement.
Description of drawings
Fig. 1 is the schematic flow sheet of the big temperature difference compression type heat of two-stage series connection of the present invention pump assembly embodiment.
Fig. 2 is the schematic flow sheet of three grades of series large temperature difference compression type heat pump assembly embodiment of the present invention.
Fig. 3 is the schematic flow sheet of multistage (greater than three grades) of the present invention big temperature difference compression type heat pump assembly embodiment.
Fig. 4 is the schematic flow sheet of the big temperature difference compression type heat pump assembly embodiment of final stage band open type economizer of the present invention.
Fig. 5 is the schematic flow sheet of the big temperature difference compression type heat pump assembly embodiment of final stage band closed economy device of the present invention.
Number in the figure: 1a-first order condenser; 1b-second level condenser; 1c-third level condenser; 1m-m level condenser; 1n-n level condenser; 2a-first evaporator; 2b-second level evaporimeter; 2c-third evaporator; 2m-m level evaporimeter; 2n-n level evaporimeter; 3a-first order compressor; 3b-high stage compressor; 3c-third level compressor; 3m-m stage compressor; 3n-final stage compressor; 4a-first order condensator outlet cryogen throttling arrangement; 4b-second level condensator outlet cryogen throttling arrangement; 4c-third level condensator outlet cryogen throttling arrangement; 4m-m level condensator outlet cryogen throttling arrangement; 4n-last condenser stage outlet cryogen throttling arrangement; 5a-first evaporator outlet cryogen throttling arrangement; 5b-second level evaporator outlet cryogen throttling arrangement; 5c-third evaporator outlet cryogen throttling arrangement; 5m-m level evaporator outlet cryogen throttling arrangement; 5n-final evaporator outlet cryogen throttling arrangement; 6-economizer; 7-economizer throttling arrangement.
The specific embodiment
Technical scheme of the present invention is to adopt plural serial stage to combine source pump, and promptly unit is made up of two-stage or the above compressor of two-stage, condenser, evaporimeter, throttling arrangement etc.Condenser hot water lines at different levels connect mutually, be about in the condensers at different levels in order to section before and after the water inlet pipe of heat exchange and the outlet pipe mutually series connection constitute the turnover loop of a connection, a shared water system, hot water are sent after the heating step by step by n level condenser successively; Evaporimeter cold water pipelines at different levels are connected mutually, be about in the evaporimeters at different levels in order to section before and after the water inlet pipe of heat exchange and the outlet pipe mutually series connection constitute the turnover loop of a connection, a shared water system, cold water are sent after the cooling step by step by n level evaporimeter successively.Be connected in series by throttling arrangement between the adjacent condenser refrigerant tubing, last condenser stage is connected by throttling arrangement with first evaporator, also be connected in series between the adjacent evaporator refrigerant pipeline by throttling arrangement, be connected by compressor between evaporimeter and the condenser, form refrigerant passage.Cold-producing medium by condensers at different levels step-down cooling condensation step by step, enters first evaporator by throttling arrangement successively at last again, more successively by evaporimeters at different levels decompression evaporation step by step; The refrigerant gas that evaporates in evaporimeters at different levels is entered corresponding condenser condenses by corresponding compressor compresses.Specifically: the saturated or superheated refrigerant steam that comes out from first evaporator is entered first order condenser by first order compressor compresses, saturated or the superheated refrigerant steam that comes out from second level evaporimeter is entered second level condenser by the high stage compressor compression, ..., the saturated or superheated refrigerant steam that comes out from final evaporator is entered last condenser stage by final stage compressor compresses; The condensation of refrigerant liquid that first order condenser comes out at first enters second level condenser by throttling arrangement, condensate liquid in the condenser of the second level enters third level condenser by throttling arrangement again ... up to the last grade condenser, enter first evaporator by throttling arrangement more at last, part evaporation back is entered first order condenser by first order compressor compresses, unevaporated liquid enters second level evaporator evaporation by throttling arrangement again, gas is entered second level condenser by the high stage compressor compression, unevaporated liquid enters third evaporator again ... one-level evaporimeter to the last, cold-producing medium all evaporates, and is entered the afterbody condenser by the afterbody compressor compresses.
Below in conjunction with specific embodiment, the specific embodiment of the present invention is described.
Embodiment 1: the big temperature difference compression type heat of two-stage series connection pump assembly
As shown in Figure 1, this source pump is made up of first evaporator 2a, first order compressor 3a, first order condenser 1a, first order condensator outlet cryogen throttling arrangement 4a, first evaporator outlet cryogen throttling arrangement 5a and second level evaporimeter 2b, high stage compressor 3b, second level condenser 1b, second level condensator outlet cryogen throttling arrangement 4b.Wherein, first order condenser 1a pressure is greater than second level condenser 1b pressure, and second level condenser 1b pressure is greater than first evaporator 2a pressure, and first evaporator 2a pressure is greater than second level evaporimeter 2b pressure.Enter first order condenser 1a from the overheated or saturated refrigerant vapour of first evaporator 2a after by first order compressor 3a compression and be condensed into refrigerant liquid, the condensation latent heat heat hot water high temperature section of being emitted; Enter second level condenser 1b from the overheated or saturated refrigerant vapour of second level evaporimeter 2b after by high stage compressor 3b compression and be condensed into refrigerant liquid, the condensation latent heat heat hot water low-temperature zone of being emitted; The refrigerant liquid that first order condenser 1a flows out enters second level condenser 1b after by first order condensator outlet cryogen throttling arrangement 4a throttling step-down, institute's liberated heat also is used for the heat hot water low-temperature zone, and with second level condenser in condensed refrigerant liquid converge the back and flow out, together by entering first evaporator 2a after the condensator outlet cryogen throttling arrangement 4b throttling step-down of the second level, the part refrigerant liquid became hot gas or saturated air from cold water high temperature section heat absorption evaporation, entered first order condenser 1a by first order compressor 3a compression again, another part refrigerant liquid flows out first evaporator, by entering second level evaporimeter 2b after the further throttling step-down of first evaporator outlet cryogen throttling arrangement 5a, become hot gas or saturated air from cold water high temperature section heat absorption evaporation, entered second level condenser by high stage compressor 3b compression again; So move in circles, finish from cold water heat absorption, the purpose of heat hot water.As can be seen, this unit has been divided into two sections respectively with hot water and cold water, hot water step in two sections condensers heats up, cold water is the step cooling in the two-stage evaporation device, condensing pressure and evaporating pressure adapt with separately hot and cold water temperature respectively, thereby reduced the irreversible heat transfer loss in evaporimeter and the condenser, system effectiveness is improved.
2: three grades of series large temperature difference compression type heats of embodiment pump assembly
As shown in Figure 2, this source pump is made up of first evaporator 2a, first order compressor 3a, first order condenser 1a, first order condensator outlet cryogen throttling arrangement 4a, first evaporator outlet cryogen throttling arrangement 5a and second level evaporimeter 2b, high stage compressor 3b, second level condenser 1b, second level condensator outlet cryogen throttling arrangement 4b, second level evaporator outlet cryogen throttling arrangement 5b and third evaporator 2c, third level compressor 3c, third level condenser 1c, third level condensator outlet cryogen throttling arrangement 4c.Wherein, first order condenser 1a pressure is greater than second level condenser 1b pressure, second level condenser 1b pressure is greater than third evaporator 1c pressure, third level condenser 1c pressure is greater than first evaporator 2a pressure, first evaporator 2a pressure is greater than second level evaporimeter 2b pressure, and second level evaporimeter 2b pressure is greater than third evaporator 2c pressure.Enter first order condenser 1a from the overheated or saturated refrigerant vapour of first evaporator 2a after by first order compressor 3a compression and be condensed into refrigerant liquid, the condensation latent heat heat hot water high temperature section of being emitted; Enter second level condenser 1b from the overheated or saturated refrigerant vapour of second level evaporimeter 2b after by high stage compressor 3b compression and be condensed into refrigerant liquid, the condensation latent heat heat hot water middle-temperature section of being emitted; Enter third level condenser 1c from the overheated or saturated refrigerant vapour of third evaporator 2c after by third level compressor 3c compression and be condensed into refrigerant liquid, the condensation latent heat heat hot water low-temperature zone of being emitted; The refrigerant liquid that first order condenser 1a flows out enters second level condenser 1b after by first order condensator outlet cryogen throttling arrangement 4a throttling step-down, institute's liberated heat also is used for the heat hot water middle-temperature section, and with second level condenser in condensed refrigerant liquid converge the back and flow out, together by entering third level condenser 1c after the condensator outlet cryogen throttling arrangement 4b throttling step-down of the second level, institute's liberated heat also is used for the heat hot water low-temperature zone, and with third level condenser 1c in condensed refrigerant liquid converge the back and flow out, together by entering first evaporator 2a after the third level condensator outlet cryogen throttling arrangement 4c throttling step-down, the part refrigerant liquid became hot gas or saturated air from cold water high temperature section heat absorption evaporation, entered first order condenser 1a by first order compressor 3a compression again, another part refrigerant liquid flows out first evaporator, by entering second level evaporimeter 2b after the further throttling step-down of first evaporator outlet cryogen throttling arrangement 5a, the part refrigerant liquid became hot gas or saturated air from cold water middle-temperature section heat absorption evaporation, was entered second level condenser by high stage compressor 3b compression again; Remaining refrigerant liquid flows out second level evaporimeter again, by entering third evaporator 2c after the further throttling step-down of second level evaporator outlet cryogen throttling arrangement 5b, become hot gas or saturated air from cold water low-temperature zone heat absorption evaporation, entered third level condenser by third level compressor 3c compression again; So move in circles, finish from cold water heat absorption, the purpose of heat hot water.As can be seen, this unit has been divided into three sections respectively with hot water and cold water, hot water step in three sections condensers heats up, cold water is the step cooling in three sections evaporimeters, condensing pressure and evaporating pressure adapt with separately hot and cold water temperature respectively, thereby reduced the irreversible heat transfer loss in evaporimeter and the condenser, system effectiveness is improved.
In addition, if the temperature difference of cold water and hot water is bigger, or the capacity of unit is bigger, in order further to improve the unit performance coefficient, can consider to adopt the more unit of progression, as shown in Figure 3, total n group condenser, evaporimeter, compressor and corresponding throttling arrangement and connecting line are formed.Condenser hot water lines at different levels connect mutually, be about in the condensers at different levels in order to section before and after the water inlet pipe of heat exchange and the outlet pipe mutually series connection constitute the turnover loop of a connection, a shared water system, hot water are sent after the heating step by step by n level condenser successively; Evaporimeter cold water pipelines at different levels are connected mutually, be about in the evaporimeters at different levels in order to section before and after the water inlet pipe of heat exchange and the outlet pipe mutually series connection constitute the turnover loop of a connection, a shared water system, cold water are sent after the cooling step by step by n level evaporimeter successively.Be connected in series by throttling arrangement between the condenser refrigerant side, last condenser stage is connected by throttling arrangement with first evaporator; Also be connected in series between the evaporator refrigerant side by throttling arrangement; Be connected by compressor between evaporimeter and the condenser, form refrigerant passage.Cold-producing medium is successively by condensers at different levels step-down cooling condensation step by step, enter first evaporator by throttling arrangement more at last, again successively by evaporimeters at different levels decompression evaporation step by step, that is to say, in the condensers at different levels, the previous stage condenser pressure is greater than the next stage condenser pressure, in the evaporimeters at different levels, the previous stage evaporator pressure is greater than the next stage evaporator pressure, and last condenser stage pressure is greater than first evaporator pressure; The refrigerant gas that evaporates in evaporimeters at different levels is entered corresponding condenser condenses by corresponding compressor compresses.Specifically: the saturated or superheated refrigerant steam that comes out from first evaporator is entered first order condenser by first order compressor compresses, saturated or the superheated refrigerant steam that comes out from second level evaporimeter is entered second level condenser by the high stage compressor compression, ..., the saturated or superheated refrigerant steam that comes out from n level evaporimeter is entered n level condenser by the compression of n stage compressor; The condensation of refrigerant liquid that first order condenser comes out at first enters second level condenser by throttling arrangement, condensate liquid in the condenser of the second level enters third level condenser by throttling arrangement again ... up to the last grade condenser, enter first evaporator by throttling arrangement more at last, part evaporation back is entered first order condenser by first order compressor compresses, unevaporated liquid enters second level evaporator evaporation by throttling arrangement again, gas is entered second level condenser by the high stage compressor compression, unevaporated liquid enters third evaporator again ... one-level evaporimeter to the last, cold-producing medium all evaporates, and is entered the afterbody condenser by the afterbody compressor compresses.
In order further to improve the efficiency of energy utilization of source pump, can economizer 6 be set in final stage, economizer can adopt open type economizer or closed economy device.Figure 4 shows that the big temperature difference compression type heat of the plural serial stage pump assembly that the open type economizer is set in final stage, flash gas path pipeline is connected with the intergrade of final stage compressor.The liquid refrigerant that from last condenser stage, flows out, flow into the economizer chamber through joint economizer stream device 7, the gas of shwoot enters the intergrade of final stage compressor 3n through pipeline in throttling process, as the usefulness of middle aerating with cooling, remaining liquid refrigerant is cooled to the saturation temperature under the intermediate pressure, again by entering first evaporator 2a after the final stage throttling arrangement 4n throttling for the second time.Other cyclic processes are the same.Figure 5 shows that the big temperature difference compression type heat of the plural serial stage pump assembly that the closed economy device is set in final stage, flash gas path pipeline is connected with the intergrade of final stage compressor.The liquid refrigerant that from last condenser stage, flows out, a part is through 7 flash distillations of economizer throttling arrangement, make all the other cold-producing mediums cold excessively, the refrigerant gas of evaporation enters the intergrade recompression of final stage compressor 3n, and cold excessively refrigerant liquid enters first evaporator 2a by final stage throttling arrangement 4n.Other cyclic processes are the same.
Claims (2)
1, the big temperature difference compression type heat of a kind of plural serial stage pump assembly is characterized in that: this unit is made up of two-stage or the condenser more than the two-stage, evaporimeter, compressor and corresponding throttling arrangement and connecting line; Condenser hot water lines at different levels connect mutually, are about in the condensers at different levels in order to section series connection mutually before and after the water inlet pipe of heat exchange and the outlet pipe, and a shared water system, hot water line's import and outlet are separately positioned in last condenser stage and the first order condenser; Evaporimeter cold water pipelines at different levels are connected mutually, are about in the evaporimeters at different levels in order to section series connection mutually before and after the water inlet pipe of heat exchange and the outlet pipe, and a shared water system, the import of cold water pipeline and outlet are separately positioned in first evaporator and the final evaporator; Be connected in series by condensator outlet cryogen throttling arrangement between the adjacent condenser refrigerant line, last condenser stage is connected by last condenser stage outlet cryogen throttling arrangement with first evaporator; Be connected in series by evaporator outlet cryogen throttling arrangement between the adjacent evaporator refrigerant pipeline; Be connected by compressor with between one-level evaporimeter and the condenser, form refrigerant passage.
2, the big temperature difference compression type heat of a kind of plural serial stage according to claim 1 pump assembly, it is characterized in that: between last condenser stage and first evaporator, economizer is set, flash gas path pipeline is connected with the intergrade of final stage compressor, and described economizer adopts open type economizer or closed economy device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB200710099607XA CN100491866C (en) | 2007-05-25 | 2007-05-25 | Multistage-cascaded compression type heat pump set under large temperature difference |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB200710099607XA CN100491866C (en) | 2007-05-25 | 2007-05-25 | Multistage-cascaded compression type heat pump set under large temperature difference |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101093116A CN101093116A (en) | 2007-12-26 |
| CN100491866C true CN100491866C (en) | 2009-05-27 |
Family
ID=38991499
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200710099607XA Expired - Fee Related CN100491866C (en) | 2007-05-25 | 2007-05-25 | Multistage-cascaded compression type heat pump set under large temperature difference |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100491866C (en) |
Families Citing this family (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101988771B (en) * | 2009-07-30 | 2013-01-23 | 阜新金昊空压机有限公司 | Nitrogen cooling device for preventing fire-extinguishing in high-temperature environment |
| CN101922800A (en) * | 2010-09-27 | 2010-12-22 | 江苏天舒电器有限公司 | Counter-flow multi-level condensation heat pump water heater |
| JP5754935B2 (en) * | 2010-12-24 | 2015-07-29 | 荏原冷熱システム株式会社 | Compression refrigerator |
| CN102679546A (en) * | 2012-05-24 | 2012-09-19 | 广州市设计院 | Efficient high-temperature hot-water heat pump unit |
| CN103673059A (en) * | 2013-11-08 | 2014-03-26 | 清华大学 | Compression-type heat exchanger unit |
| CN104266399B (en) * | 2014-10-16 | 2017-03-22 | 珠海格力电器股份有限公司 | Heat pump system |
| CN106369858B (en) * | 2015-12-30 | 2020-11-03 | 李华玉 | First-class thermally-driven compression heat pump |
| CN105928036A (en) * | 2016-06-25 | 2016-09-07 | 王清正 | Centralized large-temperature-difference heating system |
| CN106524741B (en) * | 2016-12-16 | 2022-03-01 | 江苏天舒电器股份有限公司 | Heat pump type double-circulation hot air drying system and control method thereof |
| CN109708337B (en) * | 2019-03-04 | 2021-10-01 | 北京热科能源技术研究有限公司 | Multistage series compression heat pump unit |
| CN110068219A (en) * | 2019-03-15 | 2019-07-30 | 南京航空航天大学 | Analysis of Heat Pump Drying System and its working method with heat-storing device |
| CN110486943A (en) * | 2019-09-05 | 2019-11-22 | 天津商业大学 | The not exclusively cooling moderate and high temperature heat system of throttling among the more condensers of multi-stage compression |
| CN111271752A (en) * | 2020-02-14 | 2020-06-12 | 同济大学 | Multi-heat exchanger serial transcritical CO2Heat pump heating system |
| CN111795423B (en) * | 2020-03-26 | 2021-09-03 | 同济大学 | Carbon dioxide heat pump heating system based on three-fluid heat exchanger |
| CN111550943A (en) * | 2020-04-26 | 2020-08-18 | 珠海格力电器股份有限公司 | Secondary throttling double-condensation refrigerating system, air conditioner and control method |
| CN111550944B (en) * | 2020-04-26 | 2024-03-29 | 珠海格力电器股份有限公司 | Triple throttling enthalpy-increasing double-condensation refrigerating system, air conditioner and control method |
| CN111623546A (en) * | 2020-04-26 | 2020-09-04 | 珠海格力电器股份有限公司 | Triple throttling enthalpy-increasing double-condensation refrigerating system, air conditioner and control method |
| CN111550942A (en) * | 2020-04-26 | 2020-08-18 | 珠海格力电器股份有限公司 | Double-enthalpy-increasing double-condensing three-stage compression refrigeration system, air conditioner and control method |
| CN114909824A (en) * | 2021-02-10 | 2022-08-16 | 上海本家空调系统有限公司 | Condenser parallel compression steam unit |
-
2007
- 2007-05-25 CN CNB200710099607XA patent/CN100491866C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN101093116A (en) | 2007-12-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100491866C (en) | Multistage-cascaded compression type heat pump set under large temperature difference | |
| US6519967B1 (en) | Arrangement for cascade refrigeration system | |
| CN101000180B (en) | Two-stage and three-stage absorption refrigeration machine | |
| CN105546863A (en) | Auto-cascade single-temperature or double-temperature refrigeration cycle system adopting ejector for synergism | |
| CN109708337B (en) | Multistage series compression heat pump unit | |
| CN101226013B (en) | Grade compression-segmenting heat-taking type steam compression heat pump | |
| CN101825372A (en) | Device and method for combined ejection refrigeration and vapor compression refrigeration cycle | |
| CN105546864A (en) | Auto-cascade vapor compression type refrigeration cycle system with evaporation subcooler | |
| CN203177524U (en) | Heat exchange system with multi-section lithium bromide absorption-type unit | |
| CN100501267C (en) | Plural serial stage waterway single heating type heat pump water heating machine | |
| CN101413739A (en) | Double-effect heat pump circulation three-effect heat exchanger | |
| CN101871702B (en) | Double heat source high-efficiency absorption refrigerating plant | |
| CN108759139B (en) | Primary throttling intermediate incomplete cooling refrigeration system with intermediate temperature evaporator | |
| CN109386980B (en) | Cold and hot energy utilization system | |
| CN108036445B (en) | Improved heat source tower heat pump device | |
| CN101737998B (en) | Absorption type refrigerating unit for fully recovering waste heat | |
| CN109442804B (en) | Double-stage compression heat pump circulation system for deep condensation of exhaust steam | |
| CN109682103A (en) | Refrigeration system of the direct condensation by contact of single stage compress with injector | |
| CN201837138U (en) | Triple-serial-connection compression heat pump system with large temperature difference | |
| CN209230074U (en) | A kind of two-stage compression heat pump circulatory system of deep condensation steam exhaust | |
| CN115289702A (en) | Heat exchange system | |
| CN211120095U (en) | Double-evaporator refrigeration system with double ejectors for efficiency improvement | |
| CN209672631U (en) | Refrigeration system of the direct condensation by contact of single stage compress with injector | |
| CN108759156B (en) | Secondary throttling middle incomplete cooling two-stage compression heat pump system | |
| CN112413866A (en) | Condensate water recycling assembly and air conditioning system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Beijing Xin Ling hi tech air conditioning equipment Co., Ltd.|Zhang Meixian Assignor: Tsinghua University Contract record no.: 2010110000197 Denomination of invention: Multistage-cascaded compression type heat pump set under large temperature difference Granted publication date: 20090527 License type: Exclusive License Open date: 20071226 Record date: 20101111 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090527 Termination date: 20160525 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |